WO2004104545A1 - Load measuring device for rolling bearing unit and load masuring rolling bearing unit - Google Patents

Load measuring device for rolling bearing unit and load masuring rolling bearing unit Download PDF

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Publication number
WO2004104545A1
WO2004104545A1 PCT/JP2004/006410 JP2004006410W WO2004104545A1 WO 2004104545 A1 WO2004104545 A1 WO 2004104545A1 JP 2004006410 W JP2004006410 W JP 2004006410W WO 2004104545 A1 WO2004104545 A1 WO 2004104545A1
Authority
WO
WIPO (PCT)
Prior art keywords
rolling elements
bearing unit
revolution
rolling bearing
ring
Prior art date
Application number
PCT/JP2004/006410
Other languages
English (en)
French (fr)
Inventor
Takeshi Takizawa
Tomoyuki Yanagisawa
Koichiro Ono
Ikunori Sakatani
Original Assignee
Nsk Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nsk Ltd. filed Critical Nsk Ltd.
Priority to US10/535,936 priority Critical patent/US7320257B2/en
Priority to EP04731482.8A priority patent/EP1625376B1/en
Publication of WO2004104545A1 publication Critical patent/WO2004104545A1/en

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Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings
    • G01M13/045—Acoustic or vibration analysis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/007—Encoders, e.g. parts with a plurality of alternating magnetic poles
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
    • G01P3/00—Measuring linear or angular speed; Measuring differences of linear or angular speeds
    • G01P3/42—Devices characterised by the use of electric or magnetic means
    • G01P3/44—Devices characterised by the use of electric or magnetic means for measuring angular speed
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
    • G01P3/00—Measuring linear or angular speed; Measuring differences of linear or angular speeds
    • G01P3/42—Devices characterised by the use of electric or magnetic means
    • G01P3/44—Devices characterised by the use of electric or magnetic means for measuring angular speed
    • G01P3/443—Devices characterised by the use of electric or magnetic means for measuring angular speed mounted in bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the present invention relates to a load measuring device for a rolling bearing unit and a load measuring rolling bearing unit, for example, a rolling bearing unit used to support wheels of a mobile body such as a car, a railway vehicle, various carrier cars, and so forth. More particularly, the present invention relates to a load measuring device for a rolling bearing unit and a load measuring rolling bearing unit, which can secure a running stability of a mobile body by measuring at least one of a radial load and an axial load applied to the rolling bearing unit.
  • the rolling bearing unit isusedto support rotatably the wheel of the vehicle with the suspension system. Also, the rotational speed of the wheel must be sensed to control various vehicle attitude stabilizing system such as the anti-lock brake system (ABS) , the traction control system (TCS) , andsoon. Asaresult, recently not only to support rotatably the wheel with the suspension system but also to sense the rotational speed of this wheel is widely carried out by the rolling bearing unit equipped with the rotational speed detection device in which the rotational speed detection device is incorporated into the rolling bearing unit.
  • ABS anti-lock brake system
  • TCS traction control system
  • Asaresult recently not only to support rotatably the wheel with the suspension system but also to sense the rotational speed of this wheel is widely carried out by the rolling bearing unit equipped with the rotational speed detection device in which the rotational speed detection device is incorporated into the rolling bearing unit.
  • the rolling bearing unit equipped with the rotational speed detection device used for such purpose, a number of structures such as the structure set forth in JP-A-2001-21577, etc. are known.
  • the ABS or the TCS can be controlled appropriately by feeding a signal indicating the rotational speed of the wheel, which is sensed by the rolling bearing unit equipped with the rotational speed detection device, to the controller.
  • the stability of the running attitude of the vehicle at the time of braking or acceleration can be assured by the rolling bearing unit equipped with the rotational speed detection device, nevertheless the brake and the engine must be controlled based on full information, which have an influence on the running stability of the vehicle, to assure this stability under more severe conditions.
  • the rolling bearing unit equipped with the load measuring device shown in FIG.37 is disclosed in JP-A-2001-21577.
  • a hub 2 is fitted to the inner diameter side of an outer ring 1.
  • Such hub 2 c ⁇ uples/fixes the wheel and acts as a rotating ring and also an inner-ring equivalent member.
  • Such outer ring 1 is supported with the suspension system and acts as a stationary ring and also an outer-ring equivalent member .
  • This hub 2 includes a hub main body 4 having a rotation side flange 3 at its outer end portion (end portion positioned on the out side in a width direction in a fitted state to the vehicle) to fix the wheel, and an inner ring 6 fitted to an inner end portion (end portion positioned on the center side in the width direction in the fitted state to the vehicle) of the hub main body 4 and fixed with a nut 5. Then, a plurality of rolling elements 9a, 9b are aligned respectively between double row outer ring raceways 7, 7 and double row inner ring raceways 8, 8. Such double row outer ring raceways 7, 7 are formed on an inner peripheral surface of the outer ring 1 to act as a stationary side raceway respectively. Such double row inner ring raceways 8, 8 are formed on an outer peripheral surface of the hub 2 to act as a rotation side raceway respectively, such that the hub 2 can be rotated on the inner diameter side of the outer ring 1.
  • a fitting hole 10 for passing through the outer ring 1 in the diameter direction is formed in a middle portion of the outer ring 1 in the axial direction between the double row outer ring raceways 7, 7 and in an upper end portion of the outer ring 1 in the almost perpendicular direction.
  • a round lever (rod-like) displacement sensor 11 serving as a load measuring sensor is fitted into the fitting hole 10.
  • the displacement sensor 11 is of non-contact type, and a sensing face provided to its top end surface (lower end surface) is opposed closely to an outer peripheral surface of a sensor ring 12 that is fitted to the middle portion of the hub 2 in the axial direction.
  • the displacement sensor 11 outputs a signal in response to an amount of change in the distance.
  • the load applied to the rolling bearing unit can be measured based on a sensed signal of the displacement sensor 11.
  • the outer ring 1 supported with the suspension system of the vehicle is pushed down by the weight of the vehicle whereas the hub 2 for supporting/fixing the wheel still acts to stay at that position as it is . Therefore, a deviation between a center of the outer ring 1 and a center of the hub 2 is increased based on elastic deformations of the outer ring 1, the hub 2, and the rolling elements 9a, 9b as the weight is increased more and more.
  • the load applied to the rolling bearing unit which is equipped with the displacement sensor 11 can be calculated based on a relational expression derived by the experiment or the like previously, a map, or the like. Based on the loads applied to the rolling bearing units and sensed in this manner, the ABS can be controlled properly and also the driver is informed of the improper carrying state .
  • the related-art structure shown in FIG.37 can sense a rotational speedofthe hub 2 in addition to the radial load applied to the rolling bearing unit.
  • a rotational speed encoder 13 is fitted/fixed to the inner end portion of the inner ring 6 and also a rotational speed sensor 15 is secured to a cover 14 that is put on an inner end opening portion of the outer ring 1. Then, a sensing portion of the rotational speed sensor 15 is opposed to a sensed portion of the rotational speed encoder 13 via a sensing clearance.
  • an output of the rotational speed sensor 15 is changed when the rotational speed encoder 13 is revolved together with the hub 2, to which the wheel is fixed, and then the sensed portion of such rotational speed encoder 13 passes through in vicinity of the sensed portion of the rotational speed sensor 15.
  • a frequency of an output of the rotational speed sensor 15 is in proportion to the number of revolution of the wheel. Therefore, if the output signal of the rotational speed sensor 15 is supplied to the controller (not shown) provided to the vehicle body side, the ABS or the TCS can be controlled appropriatel .
  • the related-art structure set forth in above JP-A-2001-21577 measures the radial load applied to the rolling bearing unit whereas, in JP-A-3-209016, the structure for measuring a magnitude of the axial load applied to the rolling bearing unit via the wheel is set forth.
  • the rotation side flange 3 used to support the wheel is fixed to an outer peripheral surface of an outer end portion of a hub 2a that acts as the rotating ring and the inner ring equivalent member.
  • double row inner ring raceways 8, 8 that correspond to a rotation side raceway respectively are formed on an outer peripheral surface of the middle portion or the inner end portion of the hub 2a.
  • a stationary side flange 17 to support/fix the outer ring 1 to a knuckle 16 constituting the suspension system is fixed to an outer peripheral surface of the outer ring 1, which is arranged around the hub 2a in a concentric manner with this hub 2a and acts as the stationary ring and the outer ring equivalent member.
  • the double row outer ring raceways 7, 7 that correspond to a stationary side raceway respectively are formed on the inner peripheral surface of the outer ring 1.
  • a plurality of rolling elements (balls) 9-a, 9b are provided rotatably between the outer ring raceways 7, 7 and- the inner ring raceways 8 , 8 respectively, whereby the hub 2a is supported rotatably on the inner diameter side of the outer ring 1.
  • a load sensor 20 is affixed to portions that surround screwed holes 19, into which a bolt 18 is screwed respectively to couple the stationary side flange 17 with the knuckle 16, at plural locations on the inner side surface of the stationary side flange 17 respectively. In a state that the outer ring 1 is supported/fixed to the knuckle 16, these load sensors 20 are held between the outer surface of the knuckle 16 and the inner surface of the stationary side flange 17.
  • the load applied to the rolling bearing unit is measured by measuring respective displacements of the outer ring 1 and the hub 2 in the radial direction by means of the displacement sensor 11.
  • a high-precision sensor must be used as the displacement sensor 11 to measure the load with good precision. Since a high-precision non-contact type sensor is expensive, it is inevitable that a cost is increased as the overall rolling bearing unit equipped with the load measuring device .
  • the load sensors 20 must be provided to the knuckle 16 as many as the bolts 18 used to support/fix the outer ring 1. For this reason, in addition to the fact that the load sensor 20 itself is expensive, it is inevitable that a cost of the overall load measuring device for the rolling bearing unit is considerably increased. Also, in the method set forth in JP-B-62-3365, the rigidity of the outer ring equivalent member must be reduced partially and thus there is such a possibility that it is difficult to assure the endurance of the outer ring equivalent member.
  • An object of the present invention is to provide a load measuring device for a rolling bearing unit and a load measuring rolling bearing unit, capable of being constructed at a low cost with no trouble with endurance and also measuring one or both of the radial load and the axial load applied to the wheel while assuring a precision required to control. Also, another object of the present invention is to provide a structure that can sense precisely the axial load applied to the rolling bearing unit by using only an output signal of a sensor provided to a rolling bearing unit portion.
  • a load measuring device for a rolling bearing unit comprises: a stationary ring having two rows of raceways; a rotating ring arranged concentrically with the stationary ring, the rotating ring having two rows of raceways which are formed respectively to be opposite to the raceways of the stationary ring; a plurality of rolling elements provided rotatably between the raceways of the stationary ring and the rotating ring, wherein contact angles of the rolling elements are directed mutually oppositely between a pair of raceways formed on the stationary ring and the rotating ring which are opposite to each other and the other pair of raceways formed on the stationary ring and the rotating ring which are opposite to each other; a pair of revolution speed sensors for sensing revolution speeds of the rolling elements in the two rows respectively; and a calculator for calculating a load applied between the stationary ring and the rotating ring based on sensed signals fed the revolution speed sensors.
  • a- load measuring rolling bearing unit comprises : a stationary ring having two rows of raceways ; a rotating ring arranged concentrically with the stationary ring, the rotating ring having two rows of raceways which are formed respectively to be opposite to the raceways of the stationary ring; a plurality of rolling elements provided rotatably between the raceways of the stationary ring and the rotating ring, wherein contact angles of the rolling elements are directed mutually oppositely between a pair of raceways formed on the stationary ring and the rotating ring which are opposite to each other and the other pair of raceways formed on the stationary ring and the rotating ring which are opposite to each other; and a pair of revolution speed sensors for sensing revolution speeds of the rolling elements in the two rows respectively.
  • the load measuring device for the rolling bearing unit and the load measuring rolling bearing unit of the present invention constructed as above is capable of measuring the load (one or both of the radial load and the axial load) loaded to the rolling bearing unit by sensing the revolution speeds of the rolling elements in a pair of rows, direction of the contact angles of which are different mutually, respectively.
  • the contact angles of the rolling elements balls
  • the revolution speeds of the rolling elements are changed when the contact angles are changed.
  • the revolution speeds of the rolling elements in the row positioned on the side that supports the axial load are decelerated while the revolution speeds of the rolling elements in the row positioned on the opposite side are accelerated in the case that the outer ring equivalent member is the rotating ring.
  • the revolution speeds of the rolling elements in the row positioned on the side that supports the axial load are accelerated while the revolution speeds of the rolling elements in the row positioned on the opposite side are decelerated in the case that the inner ring equivalent member is the rotating ring.
  • the revolution speeds of the rolling elements in respective rows are changed in response to the radial load. Therefore, the radial load applied to the rolling bearing unit can be detected by measuring change in the revolution speeds of the rolling elements in tow rows.
  • the revolution speeds of the rolling elements in a pair of rows, directions of the contact angles of which are different mutually, are sensed, a measuring precision of the radial load can be improved by eliminating the influence of the axial load.
  • the revolution speeds of the rolling elements in one row and the revolution speeds of the rolling elements in the other row are changed in the opposite direction mutually (one is increased and the other is decreased) . Therefore, the influence of the axial load upon a measured value of the radial load can be suppressed small by adding or multiplying these revolution speeds of the rolling elements in both rows.
  • the axial load applied to the rolling bearing unit can be detected by measuring change in the revolution speeds of the rolling elements in two rows.
  • the rolling bearing unit is used in a state that the rotational speed of the rotating ring is always constant, only the revolution speed sensors for sensing the revolution speeds of the rolling elements in respective rows are required for the revolution sensors used to calculate the load.
  • the axial load and the radial load can be measured based -on the rotational speed of the rotating ring sensed by the rotational speed sensor and the revolution speeds.
  • the inexpensive speed sensors used widely to get the control signals of ABS or TCS in the related art can be used as the revolution speed sensors used to measure the revolution speeds. For this reason, the overall load measuring device for the rolling bearing unit can be constructed inexpensively.
  • the load measuring device can be constructed at a relatively low cost, such load measuring device can measure the load such as the radial load, the axial load, etc. applied to the rotating member of the wheels, etc. while keeping a precision required for the control.
  • the load measuring device of the present invention can contribute to higher performance of various vehicle running stabilizing devices or various machine equipments.
  • the load measuring device of the present invention further comprises a rotational speed sensor for sensing a rotational speed of the rotating ring.
  • At least one sensor of the pair of revolution speed sensors and the rotational speed sensor may be a passive type magnetic sensor that is formed by winding a coil around a yoke made of magnetic material.
  • the magnetic sensor whose output is changed in response to change in the magnetic characteristic of the revolution speed encoder rotated together with the revolution of the rolling elements or the rotational speed encoder rotated together with the rotating ring should be employed as the revolution speed sensors and the rotational speed sensor used to implement the present invention.
  • the magnetic sensor there are the active type into which the magnetic sensing element such as Hall element, magnetoresistive element, or the like, whose characteristics are changed in response to change in the magnetism, is incorporated and the above passive type in the related art.
  • the active type that can assure an amount of change in output from the low-speed rotation is preferable in an aspect to measure exactly the revolution speed or the rotational speed of the low-speed rotation, but is expensive at present rather than the passive type sensor.
  • the passive type of a relatively low cost is used as a part of sensors that are not particularly important to assure the reliability in sensing the speed in the low-speed rotation (e.g., revolution speed sensor) , a cost of the overall load measuring system for the rolling bearing unit can be suppressed.
  • the sensor equipped with the permanent magnet and the no-magnetized encoder can be used in combination to reduced a cost.
  • the encoder which is made of magnetic material such as iron, or the like and on a sensed surface of which through holes or unevennesses are provided alternately at an equal interval in the circumferential direction may be employed.
  • the encoder in which unevennesses are provided alternately at an equal interval on a sensed surface of a retainer made of iron in the circumferential direction, or the encoder in which unevennesses are provided similarly on a sensed surface of the retainer made of synthetic resin and then magnetic material is plated on the uneven surface may be employed.
  • At least one sensor of the pair of revolution speed sensors and the rotational speed sensor may be a resolver.
  • the resolver is used as the sensor, the number of times of output change of the sensor (the number of pulses) per revolution can be increased rather than the active type or passive type magnetic sensor. As a result, a responsibility to sense the revolution speed or the rotational speed can be improved (a sensing timing of the revolution speed or the rotational speed can be set closer to a real time) and thus the running stability of the mobile body can be assured based on the measured load with higher precision.
  • the pair of revolution speed sensors and the rotational speed sensor are provided at an interval in an axial direction of the stationary ring so as to put the rolling elements in one row between the pair of revolution speed sensors and the rotational speed sensor.
  • the pair of revolution speed sensors are fitted to center portions of the stationary ring in the axial direction between a pair of rows of the rolling elements, and the rotational speed sensor is fitted to an end portion of the stationary ring in the axial direction.
  • an inner diameter ofthe fitting hole formed in the stationary ring to install a pair of revolution speed sensors therein can be suppressed small and also assurance of the rigidity and the strength of the stationary ring can be facilitated.
  • a pair of revolution speed sensors and the rotational speed sensor are fitted to a top end portion of a single sensor unit fixed to the stationary ring between a pair of rows of the rolling elements. Then, a fitted position of the rotational speed sensor is deviated closer to a rotating ring side than the revolution speed sensors in a diameter direction of the stationary ring.
  • magnetic interference between a pair of revolution speed sensors and the rotational speed sensor can be suppressed small and also the reliability in sensing the revolution speed and the rotational speed can be improved.
  • an inner diameter of the fitting hole formed in the stationary ring to install the sensor unit therein can be suppressed small and also assurance of the rigidity and the strength of the stationary ring can be made easy.
  • the stationary ring includes a connector for connecting a plug, the plug being provided to an end portion of a harness fortakingout the sensed signals of respective sensors .
  • the harness is fitted to the rolling bearing unit by fitting the rolling bearing unit equipped with respective sensors constituting the load measuring device to the suspension system and then connecting the plug to the connector.
  • the harness becomes a bar to fit the rolling bearing unit to the suspension system, and thus the fitting operation can be facilitate and in addition generation of a trouble such as breakage of the insulating layer, disconnection, etc. in the harness canbe made hard .
  • the harness is damaged, only exchange of the harness and the plug is needed in the repairing operation and thus a cost required for the repair can be suppressed low.
  • the single sensor unit has a sensor holder for holding the respective sensors, and the connector is provided integrally with the sensor holder.
  • the connector can be fitted easily to the stationary ring.
  • control such as ABS, TCS, or the like to be executed based on the rotational speed of the rotating ring is executed based on the rotational speed of the rotating ring, which is estimated based on a sensed signal of at least one revolution speed sensor out of the revolution speed sensors .
  • a cost and an install space of the sensor itself can be achieved because of omission of the rotational speed sensor, and also a cost and an install space can be achieved because of reduction in the number of the harnesses to transmit the signal .
  • an average value of the revolution speeds of the rolling elements in two rows which is calculated based on the sensed signals of the pair of revolution speed sensors, is used as an estimated value of the rotational speed of the rotating ring.
  • the rotational speed of the rotating ring can be sensed while assuring a precision necessary for the control such as ABS, TCS, or the like.
  • the rotational speed sensor is omitted in this manner, when the axial load is calculated based on a ratio of the revolution speeds in one row and the revolution speeds in the other row, for example, estimation of the rotational speed of the rotating ring based on the sensed signals of the revolution speed sensors is not required since the axial load can be calculated irrespective of change in the rotational speed of the rotating ring.
  • the load applied between the stationary ring and the rotating ring is a radial load, for example.
  • the calculator calculates the radial load applied between the stationary ring and the rotating ring based on a sum of the revolution speed of the rolling elements in one row and the revolution speed of the rolling elements in the other row.
  • the radial load can be calculated with satisfactorily good precision.
  • the load measuring device of the present invention further comprises a rotational speed sensor for sensing a rotational speed of the rotating ring. Then, the calculator calculates the radial load applied between the stationary ring and the rotating ring based on a sensed signal fed from the rotational speed sensor and sensed signals fed from the revolution speed sensors .
  • the calculator calculates the radial load- applied between the stationary ring, and the rotating ring based on a ratio of the sum of (a) the revolution speed of the rolling elements in one row and (b) the revolution speed of the rolling elements in the other row, and the rotational speed of the rotating ring.
  • the calculator calculates the radial load applied between the stationary ring and the rotating ring based on a ratio of a product of (a) the revolution speed of the rolling elements in one row and (b) the revolution speed of the rolling elements in the other row, and a square of the rotational speed of the rotating ring .
  • the load applied between the stationary ring and the rotating ring is an axial load, for example.
  • the calculator calculates the axial load applied between the stationary ring and the rotating ring based on a ratio of the revolution speed of the rolling elements in one row and the revolution speed of the rolling elements in the other row.
  • the calculator calculates the radial load applied between the stationary ring and the rotating ring based on a difference between the revolution speed of the rolling elements in one row and the revolution speed of the rolling elements in the other row.
  • the axial load can be calculated with maintaining necessary precision so far as the rotational speed of the rotating ring is constant.
  • the load measuring device of the present invention further comprises a rotational speed sensor for sensing a rotational speed of the rotating ring. Then, the calculator calculates the axial load applied between the stationary ring and the rotating ring based on a sensed signal fed from the rotational speed sensor and sensed signals fed from the revolution speed sensors .
  • the calculator calculates the axial load applied between the stationary ring and the rotating ring based on a ratio of the difference between (a) the revolution speed of the rolling elements in one row and (b) the revolution speed of the rolling elements in the other row, and the rotational speed of the rotating ring.
  • the calculator calculates the axial load applied between the stationary ring and the rotating ring based on a synthesized signal derived by synthesizing a signal representing the revolution speed of the rolling elements in one row and a signal representing the revolution speed of the rolling elements in the other row.
  • the calculator calculates the axial load based on any one of a period and a frequency of a swell of the synthesized signal.
  • the number of harnesses for transmitting signals from a plurality of sensors provided- to the rolling bearing unit side to a controller provided to the vehicle body side can be reduced, ' and a lower cost can be attained.
  • the load measuring device of the present invention further comprises a rotational speed sensor for sensing a rotational speedof the rotating ring. Then, the calculator calculates the axial load based on a ratio of any one of the period and the frequency of the swell of the synthesized signal and the rotational speed of the rotating ring.
  • one raceway ring of the stationary ring or the rotating ring is an outer ring equivalent member
  • the other raceway ring is an inner ring equivalent member
  • respective rolling elements are balls.
  • the load applied between the outer ring equivalent member and the inner ring equivalent member can be measured with good precision while assuring a function of supporting stably the wheel.
  • the revolution speeds of the rolling elements in the two rows can be measured directly.
  • revolution speed encoder since the revolution speed encoder is omitted, reduction in weight and reduction in cost can be attained based on reduction in the number of parts .
  • revolution speeds of the rolling elements in the two rows are measured as rotational speeds of retainers for holding respective rolling elements.
  • the rotational speeds of the retainers are measured by coupling and fixing the retainer and an encoder, which is formed separately from the retainer, and concentrically mutually and opposing sensing portions of the revolution speed sensors to a sensed surface of the encoder
  • the retainer is formed integrally with an elastic member into which powders made of magnetic material are mixed and is magnetized to arrange alternately an S pole and an N pole at an equal interval on a sensed surface, whose center corresponds to a rotation center of the retainer, out of any surfaces of the retainer, and sensing portions of the revolution speed sensors are opposed to a sensed surface to measure the rotational speed of the retainer.
  • an inner diameter of the encoder is larger than an inner diameter of a fitting surface, to which the encoder is fitted, of the holder and an outer diameter of the encoder is smaller than an outer diameter of the fitting surface.
  • the structure that can measure the revolution speeds the rolling elements with good precision while preventing the interference between the encode and the stationary ring and the rotating ring can be realized.
  • the revolution speed sensors for the revolution speeds of the rolling elements in two rows respectively are arranged in a state that the sensors are shifted in a revolution direction of the rolling elements by plural pieces every row.
  • the revolution speed sensors are provided by two pieces every row on opposite positionsbyl ⁇ Odegreewithrespect to a revolution center of the rolling elements.
  • the rotational speed of the retainer i.e., the revolution speeds of the rolling elements can be exactly measured.
  • the load measuring device of the present invention further comprises a comparator for comparing contact angles of the rolling elements in each row, which are calculated by the calculator in a course of calculation of the revolution speeds of the rolling elements in each row, with a normal value, and an alarm is generated when the comparator decides that the contact angles are out of a normal range.
  • the repair can be applied by sensing application of the excessive axial load, generations of preload escapement , etc., which lead to reduction in the endurance of the rolling bearing unit, before the vehicle falls into an impossible state of running.
  • the rolling elements are made of ceramics.
  • the follow-up characteristic of change in the rotation speed of the rolling elements to the sudden variation of the revolution speeds can be improved and also the revolution speeds can be measured precisely to suppress generation of the revolution slip.
  • FIG.l is a sectional view showing s first embodiment of the present invention.
  • FIG.2 is an enlarged view of an A portion in FIG.l.
  • FIG.3 is aviewofapartofaretainer and a revolution speed sensor on the left side in FIG.2 when viewed in a diameter direction.
  • FIG.4 is a schematic view explaining an action of the present invention.
  • FIG.5 is a diagram showing relationships among a radial load, a ratio of a revolution speed of a rolling element in each row to a rotational speed of an inner ring, and an axial load.
  • FIG.6 is a diagram showing relationships among the radial load, a ratio of a sum of revolution speeds of rolling elements in each row to the rotational speed of the inner ring, and an axial load.
  • FIG.7 is a diagram showing relationships between the radial load and a ratio of the revolution speed of the rolling element in each row to the rotational speed of the inner ring.
  • FIGS.8A and 8B are diagrams showing an influence of a magnitude of a preload or the radial load upon the relationship between the axial load and the ratio of the revolution speed of the rolling element in any row when no regard is paid to variation in the preload or the radial load.
  • FIGS.9A and 9B are diagrams showing the influence of a magnitude of the preload or the radial load upon the relationship between the axial load and the ratio of the revolution speed of the rolling element in each row in the present invention.
  • FIGS .10A and 10B are diagrams showing relationships between a difference in the revolution- speeds of rolling elements in a pair of rows or a ratio of this difference to a rotational speed of a rotating ring and a magnitude of the axial load in the present invention.
  • FIG.11 is a diagram showing relationships among a ratio of the revolution speeds of the rolling elements in a pair of rows to the rotational speed of the rotating ring, a magnitude of the axial load, and a magnitude of the preload.
  • FIG.12 is a diagram showing relationships- among a ratio of a difference in the revolution speeds of the rolling elements in a pair of rows to the rotational speed of the rotating ring, a magnitude of the axial load, and a magnitude of the preload.
  • FIG.13 is a flowchart showing such a- situation that the axial load is calculated by synthesizing output signals of both revolution speed sensors when the output signals of a pair of revolution speed sensors are changed in a sine-wave fashion.
  • FIG.14 is a view showing the output signals of a pair of revolution speed sensors and- a synthesized signal in this case.
  • FIG.15 is a flowchart showing such a situation that the axial load is calculated by synthesizing output signals of both revolution speed sensors when the output signals of a pair of revolution speed sensors are changed in a pulse fashion.
  • FIG.16 is a view showing the output signals of a pair of revolution speed sensors and a synthesized signal in this case.
  • FIG.17 is a schematic view showing a revolution speed encoder and revolution speed sensors in a second embodiment of the present invention when viewed in an axial direction.
  • FIG.18 is a diagram explaining the reason why the revolution speed can be derived exactly in the second embodiment .
  • FIG.19 is a view showing, similarly to FIG.17, the case that only one revolution speed sensor is provided.
  • FIG.20 is a diagram explaining the reason why a difference in the revolution speeds derived in this case is caused.
  • FIG.21 is a sectional view showing another example of a structure in which a pair of revolution speed sensors are provided.
  • FIG.22 is a block diagram showing an example of a circuit for monitoring the revolution speed to generate an alarm when such revolution speed is wrong.
  • FIG.23 is a partial sectional view showing a fifth embodiment of the present invention.
  • FIG.24 is a partial sectional view showing a sixth embodiment of the same.
  • FIG.25 is a sectional view showing a first example of a seventh embodiment of the same.
  • FIG.26 is a sectional view showing a structure different from the seventh embodiment.
  • FIG.27 is a sectional view showing a second example of the seventh embodiment of the present invention.
  • FIG.28 is a partial sectional view showing an eighth embodiment of the same.
  • FIG.29 is a sectional view showing a first example of a ninth embodiment of the same.
  • FIG.30 is a sectional view showing a second example of the ninth embodiment of the same.
  • FIG .31 is a sectional view showing a tenth embodiment of the present invention.
  • FIG.32 is a sectional view showing a first example of an eleventh embodiment of the same.
  • FIG.33 is a sectional view showing a second example of the eleventh embodiment of the same.
  • FIG.34 is a sectional view showing a first example of a twelfth embodiment of the present invention.
  • FIG.35 is a sectional view showing a second example of the twelfth embodiment of the same.
  • FIG.36 is a sectional view showing a third example of the twelfth embodiment of the same.
  • FIG.37 is a sectional view showing a first example of the structure in the related art.
  • FIG.38 is a sectional view showing a second example of the same.
  • 1 denotes an outer ring
  • 2a denote hub
  • 3 denotes a rotation-side flange
  • 4 denotes a hub main body
  • 5 denotes a nut
  • 6 denotes am inner ring
  • 7 denotes am outer ring raceway
  • 8 denotes an inner ring raceway
  • 9, 9a, 9b denote rolling element
  • 10a denote fitting hole
  • 11 denotes a displacement sensor
  • 12 denotes a sensor ring
  • 13, 13a, 13b denote rotational speed encoder
  • 14 denotes a cover
  • 16 denotes a knuckle
  • 17 denotes a stationary side flange
  • 18 denotes a bolt
  • 19 denotes a screwed hole
  • 20 denotes a load sensor
  • 21a, 21b denote revolution speed sensor
  • 22, 22a, 22b denote retainer
  • 23, 23', 23a denote sensor unit
  • FIGS.l to 3 show s first embodiment of the present invention.
  • the present embodiment shows the case that the present invention is applied to a rolling bearing unit to support idler wheels of the car (front wheels of FR car, RR car, MR car, rear wheels of FF car) . Since the structure and the operation of this rolling bearing unit itself are similar to the related-art structure shown in above FIG.37, their redundant explanation will be omitted or simplified by affixing the same reference symbols to the same portions. Feature portions in the present embodiment will be explained mainly hereinafter.
  • the rolling elements (balls) 9a, 9b are rotatably provided in double rows (two rows) respectively between the double row angular contact inner ring raceways 8, 8 and the double row angular contact outer ring raceways 7, 7 in a state that a plurality of rolling elements are held in each row by retainers 22a, 22b respectively.
  • Such inner ring raceways 8, 8 are formed on the outer peripheral surface of the hub 2 as the rotating ring and the inner ring equivalent member to constitute the rotation side raceway respectively.
  • Such outer ring raceways 7, 7 are formed on the inner peripheral surface of the outer ring 1 as the stationary ring and the outer ring equivalent member to constitute the stationary side raceway respectively.
  • the hub 2 is supported rotatably on the inner diameter side of the outer ring 1.
  • contact angles a , ⁇ b (FIG.2) that are directed mutually in the opposite direction and have the identical magnitude are applied to the rolling elements 9a, 9b in respective rows to construct a back-to-back combination type double row angular contact ball bearing .
  • the sufficient preload is applied to the rolling elements (balls) 9a, 9b in respective rows to such an extent that such preload is not lost by the axial load applied in operation.
  • the stationary side flange 17 fixed to the outer ring 1 is supported/ fixed to the knuckle constituting the suspension system, and also a brake disk and a wheel are supported/fixed to the rotation-side flange 3 of the hub 2 by plural stud bolts and plural nuts.
  • a fitting hole 10a is formed in the middle portion of the outer ring 1 constituting such rolling bearing unit in the axial direction between the double row outer ring raceways 7, 7 to pass through this outer ring 1 in the diameter direction. Then, a sensor unit 23 is inserted into this fitting hole 10a inwardly from the outside along the diameter direction of the outer ring 1 to project a top end portion 24 of the sensor unit 23 from the inner peripheral surface of the outer ring 1. A pair of revolution speed sensors 21a, 21b and a rotational speed sensor 15b are provided to this top end portion 24.
  • the revolution speed sensors 21a, 21b are used to measure the revolution speeds of the rolling elements 9a, 9b aligned in double rows.
  • a sensing surface of these sensors is arranged on both side surfaces of the top end portion 24 in the axial direction (the lateral direction in FIGS.l and 2) of the hub 2 respectively.
  • the revolution speed sensors 21a, 21b sense the revolution speeds of the rolling elements 9a, 9b arranged in double rows as the revolution speeds of the retainers 22a, 22b.
  • rim portions 25, 25 constituting these retainers 22a, 22b are arranged on the mutual opposing side.
  • revolution speed encoders 26a, 26b formed like a circular ring respectively are affixed/ supported to mutual opposing surfaces of the rim portions 25, 25 around their full circumference.
  • the characteristics of sensed surfaces of the revolution speed encoders 26a, 26b are changed alternately at an equal interval in the circumferential direction such that the revolution speeds of the retainers 22a, 22b can be sensed by the revolution speed sensors 21a, 21b.
  • sensing surfaces of the revolution speed sensors 21a, 21b are opposed closely to mutual opposing surfaces serving as sensed surfaces of the revolution speed encoders 26a, 26b.
  • distances (sensing clearances) between the sensed surfaces of the revolution speed encoders 26a, 26b and the sensing surfaces of the revolution speed sensors 21a, 21b should be set larger than pocket clearances defined as clearances between inner surfaces of pockets in the retainers 22a, 22b and rolling contact surfaces of the rolling elements 9a, 9b but 2 mm or smaller.
  • sensing clearances are smaller than the pocket clearances, there is a possibility that the sensed surfaces and the sensing surfaces are rubbed mutually when the retainers 22a, 22b are displaced by such pocket clearances, and therefore such sensing clearances are not preferable. On the contrary, if such sensing clearances exceed 2 mm, it becomes difficult to measure precisely revolutions of the revolution speed encoders 26a, 26b by the revolution speed sensors 21a, 21b.
  • the rotational speed sensor 15b is used to measure the rotational speed of the hub 2 as the rotating ring.
  • a sensing surface of this sensor is arranged on a top end surface of the top end portion 24, i.e., an inner end surface of the outer ring 1 in the diameter direction.
  • a cylindrical rotational speed encoder 13a is fitted/fixed in the middle portion of the hub 2 between the double row angular contact inner ring raceways 8, 8.
  • a sensing surface of the rotational speed sensor 15b is opposed to the outer peripheral surface of the rotational speed encoder 13a as the sensed surface.
  • the characteristic of the sensed surface of the rotational speed encoder 13a is changed alternately at an equal interval in the circumferential direction such that the rotational speed of the hub 2 can be sensed by the rotational speed sensor 15b.
  • the sensing clearance between the outer peripheral surface of the rotational speed encoder 13a and the sensing surface of the rotational speed sensor 15b is suppressed 2 mm or smaller.
  • the encoder having various structures used in the related art to sense the rotational speed of the wheel in order to get the control signal for the ABS or the TCS may be employed.
  • the encoder made of a mutipolar magnet, in which an N pole and an S pole are arranged alternately on the sensed surface (the side surface or the outer peripheral surface) may be preferably employed as the above encoders 26a, 26b, 13a.
  • the encoder made of simple magnetic material, the encoder whose optical characteristic is changed alternately at an equal interval over the circumferential direction (if such encoder is combined with the magnetic rotational speed sensor having the permanent magnet or the optical rotational speed sensor) may also be employed.
  • revolution speed encoders 26a, 26b a circular-ring permanent magnet in which the N pole and the S pole are aligned alternately at an equal interval on the axial-direction surface as the sensed surface is employed as the above revolution speed encoders 26a, 26b.
  • Such revolution speed encoders 26a, 26b are formed by the insert molding or the two color molding (two type materials are molded simultaneously) after they are coupled/ fixed to side surfaces of the rim portions 25, 25 of the retainers 22a, 22b by the bonding or they are set in the cavity when these retainers 22a, 22b are to be injection-molded. Any method may be employed in response to a cost, bonding strength required, etc.
  • the fixing method by using the adhesive is employed, a new mold is not needed to mold the retainers 22a, 22b because the ordinary retainer in the related-art is used as the retainers 22a, 22b, and thus a cost can be suppressed from this aspect. Therefore, the fixing method by using the adhesive is effective in the case that the number of productions is relatively small and a cost must be suppressed as a whole.
  • the adhesive in this case, the epoxy adhesive or the silicone resin adhesive can be used preferably.
  • the coupling/fixing method by using the insert molding is effective in the case that the number of productions is relatively large and a cost must be suppressed as a whole.
  • the retainer formed of a synthetic resin by the injection molding is used as the retainers 22a, 22b.
  • any synthetic resin may be used if such resin may be molded by the injection molding.
  • a reinforcing agent such as glass fiber, carbon fiber, or the like should be mixed appropriately in the synthetic resin.
  • an amount of mixture of the reinforcing agent in this case about 5 to 40 wt% is appropriate. An effect of increasing the strength by the mixture is seldom expected if an amount of mixture is below 5 wt%, while toughness of resultant retainers 22a, 22b is lowered to generate readily the damage such as fragment, crack, or the like if the reinforcing agent is mixed in excess of 40 wt%.
  • an amount of mixture of the reinforcing agent is restricted in a range of about 10 to 30 wt%.
  • the circular-ring permanent magnet used as the revolution speed encoders 26a, 26b following magnets may be used. That is, the sintered magnet such as ferrite magnet, iron-neodymium magnet, samarium-cobalt magnet, or the like, the metallic magnet such as aluminum-manganese magnet, Alnico magnet, or the like, and the plastic magnet or the rubber magnet in which magnetic powders are mixed into the synthetic resin or the rubber can be employed. Because the sintered magnet and the metallic magnet give a strong magnetic force but cause the damage such as fragment, crack, or the like, the plastic magnet or the rubber magnet should be employed preferably.
  • Amixing rate of the magnetic powders into the plastic magnet or the rubber magnet is set to 20 to 95 wt%. Because the magnetic force of the magnet becomes strong as an amount of mixture is increased, an amount of mixture is adjusted in response to the magnetic force required for the revolution speed encoders 26a, 26b, while taking account of the relationship with the performance of the revolution speed sensors 21a, 21b. In this case, if an amount of mixture is set below 20 wt%, it is difficult to get the magnetic force required for the revolution speed encoders 26a, 26b irrespective of the performance of the used- revolution speed encoders 26a, 26b.
  • an amount of mixture of the magnetic powders should be set to 20 to 95 wt%, preferably 70 to 90 wt% .
  • the coupling strength between the plastic magnet and the retainer can be enhanced by forming the plastic magnet and the retainer with the same type synthetic resin.
  • the synthetic resin constituting the retainer any resin may be employed if such resin may be molded by the injection molding.
  • the synthetic resin such as PA46, PA66, PPS, or the like having the excellent heat resistance .
  • the retainer is formed separately from the encoder, it is preferable from an aspect of strength improvement in the retainer to mix the reinforcing agent such as glass fiber, carbon fiber, or the like appropriately.
  • an amount of the reinforcing agent mixed into the synthetic resin constituting the retainer is too large, toughness of the resultant retainer is lowered and the damage such as fragment, crack, or the like is easily caused. As a result, even when the reinforcing agent is mixed, an amount of mixture is restricted in a range of 5 to 40 wt%, preferably 10 to 30 wt%.
  • the magnetic powders are mixed in the above synthetic resin by about 20 to 95 wt%.
  • the magnetic powders powders of ferrite, iron-neodymium, samarium-cobalt, aluminum- manganese, Alnico, iron, or the like may be employed. If the retainer is formed while mixing such magnetic powers, the magnetic force of the magnet becomes stronger as an amount of mixture is increased. Therefore, an amount of mixture is adjusted in answer to the magnetic force required for the retainer with regard to the performance of the revolution speed sensors 21a, 21b.
  • an amount of the synthetic resin is reduced excessively if an amount of mixture is increased too much, and thus it becomes difficult to assure the strength of the resultant retainer (the toughness is lowered) .
  • a total amount of mixture of the magnetic powers and the reinforcing agent should be suppressed smaller than 98 wt%. If the magnetic powers and the reinforcing agent are mixed in total in excess of 98 wt%, the strength of the retainer is lowered and also flowability of the synthetic resin during the injection molding becomes worse, so that it is hard to get the case with good quality.
  • the retainer can be formed by molding the thermosetting resin such as the epoxy resin, or the like by means of the compression molding, independent of the event that either the retainers and the revolution speed encoders formed separately are coupled with each other or a function of the encoder is provided to the retainer itself.
  • the retainer having the excellent strength canbe obtained, but a cost is increased. Therefore, it is preferable that, if reduction in a mass-production cost is taken into consideration, the retainer should be formed of the thermosetting resin by using the injection molding in any case.
  • unevenness may be formed on a part of the retainer made of the magnetic material and then such portions may be used as the revolution speed encoder.
  • the sensor into which the permanent magnet is incorporated to generate the magnetic flux is used as the revolution speed sensors 21a, 21b.
  • unevenness canbe formed on a part of the retainer made of the permanent magnetic and also the uneven portions can be magnetized to have the S pole and the N pole.
  • the concave portions may be magnetized to have the S pole or the N pole and the convex portions may be magnetized to have the Npoleorthe Spole, otherwise only the convex portions may be magnetized to have the S pole and the N pole alternately.
  • the revolution speed sensors 21a, 21b and the rotational speed sensor 15b all being a sensor of sensing the revolution speed
  • the magnetic revolution sensor is used preferably.
  • the active type revolution sensor into which the magnetic sensing element such as Hall element, Hall IC, magnetoresistive element (MR element, GMR element) , MI element, or the like is incorporated is used preferably.
  • one side surface of the magnetic sensing element comes into contact with one end surface of the permanent magnet in the magnetization direction directly or via a stator made of magnetic material (when an encoder made of magnetic material is used)
  • theot ersidesurfaceofthe magnetic sensing element is opposed closely to the sensed surfaces of the encoders 26a, 26b, 13a directly or via the stator made of magnetic material.
  • the permanent magnetic on the sensor side is not needed since the encoder made of the permanent magnetic is used.
  • sensed signals of the above sensors 21a, 21b, 15b are input into a calculator (not shown) .
  • This calculator may be installed integrally with the rolling bearing unit by providing to the sensor unit 23 in which these sensors 21a, 21b, 15b are embedded/ supported, or the like, or may be installed separately from the rolling bearing unit on the vehicle body side. Then, this calculator calculates one or both of the radial load and the axial load applied between the outer ring 1 and the hub 2, based on the sensed signal fed from these sensors 21a, 21b, 15b.
  • the calculator in order to sense the radial load, calculates a sum of the revolution speeds of the rolling elements 9a, 9b in respective rows, which are sensed by the revolution speed sensors 21a, 21b, and then calculates the radial load based on a ratio of this sum to the rotational speed of the hub 2, which is sensed by the rotational speed sensor 15b.
  • the radial load can be sensed with good precision while suppressing small the influence of the axial load applied to the rolling bearing unit. This respect will be explained with reference to FIGS.4 to 6 hereunder. In this case, following explanation will be made under the assumption that the contact angles ⁇ a , ⁇ b of the rolling elements 9a, 9b in respective rows are set equal mutually in a state that no axial load F a is applied.
  • FIG.4 shows the applying state of the loads to the schematic rolling bearing unit for supporting the wheel shown in above FIG.l.
  • the preloads F c , F 0 are applied to the rolling elements 9a, 9b arranged in double rows between the double row inner ring raceways 8, 8 and the double row outer ring raceways 7, 7.
  • the radial load F r is applied to the rollingbearingunit by the weight of the vehicle body, etc. during operation.
  • the axial load F a is applied by the centrifugal force applied during the turning operation, etc. All the preloads F ⁇ , F o f the radial load F r , and the axial load
  • the revolution speed n c of the rolling elements 9a, 9b is changed in response to the change of the contact angles ( ⁇ a , ⁇ b ) of the rolling elements 9a, 9b, but the contact angles a , b are changed in response to the radial load F r and the axial load F a , as described above. Therefore, the revolution speed n c is changed in response to the radial load F r and the axial load F a . In the case of the present embodiment, since the hub 2 is rotated but the outer ring 1 is not rotated, particularly the revolution speed n c becomes slow with an increase of the radial load F r .
  • the radial load F r can be sensed base on the revolution speed n c .
  • the contact angles followed b the change in the revolution speed n c are changed by not only the radial load F r but also the preloads F Q , F Q and the axial load F a .
  • the revolution speed n c is changed in proportion to the rotational speed n of the hub 2. For this reason, if no regard is paid to the preloads F 0 , F 0 , the axial load F a , and the rotational speed n % , it is impossible to sense precisely the revolution speed n c .
  • the influence of the axial load F a is reduced by calculating a sum of the revolution speeds of the rolling elements 9a, 9b in respective rows sensed by the revolution speed sensors 21a, 21b.
  • the influence of the rotational speed ni of the hub 2 is eliminated by calculating the radial load F r based- on a ratio of this sum and the rotational speed ni of the hub 2 sensed by the rotational speed sensor 15b.
  • ⁇ n ca to which the revolution speed n ca of the rolling elements 9b, 9b constituting the row that do not support the axial load F a is decelerated are almost equal and their polarities are opposite (
  • FIG.6 shows relationships among a ratio ⁇ (n ca +n C b) /n ⁇ ⁇ of a sum of the revolution speeds n ca , n cb of the rolling elements 9a, 9b in both rows to the rotational speed n ⁇ of the hub 2, a magnitude of the radial load F r , and a magnitude of the axial load F a .
  • the radial load F r is sensed based on a sum of the revolution speeds n ca / n cb in both rows, the influence of the axial load F a can be suppressed minutely and also the radial load F r can sensed exactly.
  • the above explanation is made to suppress the influence of the axial load F a by adding the revolution speeds n ca , n cb in both rows.
  • the influence of the axial load F a can also be suppressed by multiplying the revolution speeds n ca , n cb in both rows (calculating a product) .
  • the revolution speeds n ca , n cb in both rows are increased or decreased to the almost same extent by the change in the axial load F a , the influence caused by the change in the axial load F a can be reduced by multiplying the revolution speeds n ca , n cb in both rows.
  • the radial ' load F r is calculated based on a ratio ⁇ (n ca Xn cb ) /n ⁇ z ⁇ of a product (n ca Xn C b) of the revolution speeds n ca , n cb in both rows to a square of the rotational speed ni of the hub.
  • the calculator calculates a difference between the revolution speeds of the rolling elements 9a, 9b in both rows sensed by the revolution speed sensors 21a, 21b and then calculates the axial load based on a ration of this difference to the rotational speed of the hub 2 sensed by the rotational speed sensor 15b.
  • the influences of the preload applied to the rolling elements 9a, 9b in bothrows andtheradial load applied to the rolling bearing unit can be suppressed small, and thus the axial load can be sensed with good precision.
  • the revolution speed n c of the rolling elements 9a, 9b is changed in response to the change in the contact angles ( a/ «b ⁇ of the rolling elements 9a, 9b.
  • the contact angles are changed in response to the axial load F a . Therefore, the revolution speed n c is changed in response to the axial load F a .
  • FIG.7 shows the changing state of the revolution speed of the rolling elements 9a, 9b in both rows with the change in the axial load F a .
  • an axis of abscissa in FIG.7 denotes a magnitude of the axial load F a and an axis of ordinate denotes a ratio n c /n ⁇ " of the revolution speed n c to the rotational speed ni of the hub 2.
  • a value representing the ratio "n c /ni" on the axis of ordinate in FIG.7 is increased downwardly in FIG.7 and decreased upwardly.
  • a solid line a indicates a ratio v *n ca / i" ' of the revolution speed n ca of the rolling elements 9a, 9 " a constituting the left side row in FIG.4 that do not support the axial load F a
  • a broken line b indicates a ratio "n C b/n ⁇ " of the revolution speed C b of the rolling elements 9b, 9b constituting the right side row in FIG. that supports the axial load F a .
  • the axial load can be detected by measuring the revolution speed n ca (n cb ) of the rolling elements 9a, 9a (or 9b, 9b) in any one row.
  • the preload Fo applied to the double row angular contact ball bearing is varied due to manufacturing errors, and also the radial load F r becomes different due to difference in the number of passengers and a carrying capacity.
  • FIG.8 shows influences of variation of the preload Fo and a magnitude of the radial load F r upon the relationship between a magnitude of the axial load F a and a ratio V n oa /ni" of the revolution speed n ca of the rolling elements 9a, 9a constituting the left side row in FIG.4 that do not support this axial load F a .
  • a solid line a , a broken line b, and a chain line c depicted in FIG.8A, 8B respectively correspond to the solid line a in FIG.5 respectively.
  • FIG.8A shows the influence of the value of the preload F 0 upon the relationship between a magnitude of the axial load F a and the ratio "n ca /ni".
  • FIG.8A shows the influence of the value of the radial load F r upon the relationship between a magnitude of the axial load F a and the ratio "n ca /ni".
  • a value on an axis of ordinate in FIG .8B representing the magnitude of the ratio ⁇ n ca /ni" is increased downwardly in FIG.8B and is decreased upwardl .
  • the value of the preload Fo is set at a middle level.
  • the revolution- speeds n ca , n cb of the rolling elements 9a, 9b on a pair of rows, magnitudes of the contact angles a , ⁇ b of which are equal (in a state that no axial load is applied) but directions of which are different mutually, are sensedby apair of revolution speed sensors 21a, 21b, and then the calculator (not shown) calculates the axial load F a based on both revolution speeds n ca ,
  • any one method of fallowing (1) to (4) is employed to sense the axial load F a based on both revolution speeds n ca , n cb .
  • the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on the ratio ⁇ n cb /n ca " of the revolution speed n cb of the rolling elements 9b, 9b in the other row to the revolution speed n ca of rolling elements 9a, 9a in one row.
  • the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on a difference "n cb -n ca " between the revolution speed n ca of rolling elements 9a, 9a in one row and the revolution speed n C b of the rolling elements 9b, 9b in the other row.
  • the axial load F a applied between the outer ring 1 and the hub 2 is calculatedbasedon a ratio " (n Cb -n ca ) /ni" of the difference "n cb -n ca " between the revolution speed n ca of rolling elements 9a, 9a in one row and the revolution speed n Cb of the rolling elements 9b, 9b in the other row to the rotational speed n ⁇ of the hub 2.
  • the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on a synthesized signal obtained by synthesizing a signal representing the revolution speed n ca of rolling elements 9a, 9a in one row and a signal representing the revolution speed n cb of the rolling elements 9b, 9b in the other row.
  • FIG.9 shows a relationship between the ratio "n cb /n ca " of the revolution speed n cb of the rolling elements 9b, 9b in the other row to the revolution speed n ca of the rolling elements 9a, 9a in one row and the axial load F a .
  • a solid line a , a broken line b, and a chain line c depicted in FIG.9A, 9B respectively show the relationship between the ratio w n Cb /n oa " and the axial load F a respectively.
  • FIG.9A shows the influence of a value of the preload F 0 applied to the rolling elements 9a, 9b upon the relationship between a magnitude of the axial load F a and the ratio "n ct ,/n ca ".
  • the solid line a indicates the case the preload F 0 is small
  • the broken line b indicates the case the preload F 0 is at a middle level
  • the chain line c indicates the case the preload F 0 is at a large level.
  • FIG.9B shows the influence of the value of the radial load F r upon the relationship between the> magnitude of the axial load- F a and the ratio ⁇ n C b/n C a".
  • the solid line a indicates the case the radial load F r is large
  • the broken line b indicates the case the radial load F r is at a middle level
  • the chain line c indicates the case the radial load F r is at a small level .
  • the ratio ⁇ n C b/n ca " of the revolution speed n C b of the rolling elements 9b, 9b in the other row to the revolution speed n ca of the rolling elements 9a, 9a in one row is increased in compliance with an increase of the axial load F a .
  • the axial load F a can be calculatedbasedon oth revolution speedsn ca , n C b-
  • the influences of the preload F 0 and the radial load F r upon the relationship between the ratio n C b/n C a" and the axial load F a are small.
  • the preload F 0 is applied uniformly to the rolling elements 9a, 9b in both rows and also the radial load F r is applied substantially uniformly. Therefore, even though the preload Fo and the radial load F r are varied, such variation affects small the calculated value of the axial load F a .
  • the preload Fo and the radial load F r have influences upon the relationship between the ratio X ⁇ n C b/n ca " and the axial load F a .
  • the rotational speed sensor 15b 15 and the rotational speed encoder 13a may be omitted since the rotational speed ni of the hub 2 is not used.
  • the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on the difference ⁇ n C b _ n C a" between the revolution speed n ca of rolling elements 9a, 9a in one row and the revolution speed n cb of the rolling elements 9b, 9b in the other row.
  • the axial load F a can be calculated- based on the difference ⁇ n cb -n ⁇ a" between both revolution speeds n ca , C b-
  • the axial load F a can be sensed precisely while suppressing the influence of the variation of the preload F 0 and the radial load F r . In this manner, if the axial load F a is derived by the method- in (2), the rotational speed sensor 15b and the rotational speed encoder 13a may be omitted since the rotational speed n ⁇ of the hub 2 is not used.
  • the axial load F a can be calculated based on the difference X ⁇ n C b-n ca " between both revolution speeds n oa , n C b •
  • the axial load F a can be detected exactly irrespective of change in the rotational speed of the hub 2 with suppressing the influence of the variations of the preload F 0 and the radial load F r .
  • the rolling bearing unit is used in the condition that the rotational speed of the rotating ring is always kept constant, like the rotation supporting portion of the machine tool or the carrier vehicle in the factory, the axial load F a can be detected exactly only by the difference "n C b-n C a" between the revolution speeds n ca , n Cb of the rolling elements 9a, 9b in both rows, like the above method in (2) .
  • the rotational speed of the rotating ring (hub 2) is changed in operation, like the rolling bearing unit used to support the wheel of the car or the railway vehicle, the difference M n C b-n C a" between the revolution speeds n ca , n cb is changed in response to this rotational speed regardless of the axial loadF a .
  • the calculator gets a synthesized signal by synthesizing (superposing) a signal representing the revolution speed n ca of the rolling elements 9a, 9a in one row, which is fed from the revolution speed sensor 21a, and a signal representing the revolution speed n cb of the rolling elements 9b, 9b in the other row, which is fed from the revolution speed sensor 21b. Then, the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on the synthesized signal.
  • the method in (4) synthesizes in advance the signals sent out from the revolution speed sensors 21a, 21b, and thus makes it possible to shorten a full length of a harness and reduce an amount of computation in the calculator.
  • FIG.11 is a diagram showing a relationship between the axial load F a and a magnitude of the preload F 0 , in addition to the relationship between the axial load F a and the ratio of the revolution speeds of the rolling elements 9a, 9b in both rows to the rotational speed of the hub 2.
  • the numerical value on the axis of ordinate is increased upwardly conversely to above FIGS.7 and 8.
  • FIG.12 is a diagram showing relationships among a ratio of a difference in the revolution speeds of the rolling elements 9a, 9b in a pair of rows to the rotational speed of the hub 2, a magnitude of the axial load F a , and a magnitude of the preload F 0 .
  • the revolution speeds n ca , n cb of the rolling elements 9a, 9b in both rows are changed in the opposite direction in answer to the axial load F a and also are accelerated as the preload F 0 is increased.
  • the above method in (4) calculates the axial load F a applied between the outer ring 1 and the hub 2, based on the ratio w (n C b-n ca ) / i" of the difference "n ch -n ca " between the revolution speeds n ca , n cb of the rolling elements 9a, 9b in a pair of rows to the rotational speed ni of the hub 2 by utilizing the relationship in FIG.12.
  • the synthesized signal is derived by the calculator to synthesize "the signals representing the revolution speeds n oa , n C b of the rolling elements 9a, 9b in both rows, which are sent out from a pair of revolution speed sensors 21a, 21b. Then, the axial load F a is calculated based on the synthesized signal and the rotational speed ni of the hub 2.
  • the method of processing the synthesized signal in this case is slightly different inthecasethatthe signals sent out from the revolution speed sensors 21a, 21b are changed like a sine wave and the case that the signals are changed like a pulse wave.
  • a synthesized signal shown in FIG .14B is obtained by synthesizing (superposing) the signals sent out from the revolution speed- sensors 21a, 21b and shown in FIG.14A respectively.
  • This synthesized signal has a swell having a swell period Ti. This swell is generated by a difference between the signals fed from the revolution speed sensors 21a, 21b, and a reciprocal (1/T ⁇ , frequency) of the swell period Ti gives a difference in frequencies of the signals sent out from the revolution speed sensors 21a, 21b.
  • the difference "n cb -n ca " between the revolution speeds n ca , n C b of the rolling elements 9a, 9b in both rows is calculated by the swell period Ti or the frequency, and then the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on the ratio " (n cb -n ca ) /n ⁇ " of the difference "n C b _ n C a to the rotational speed ni of- the hub 2.
  • the synthesis (superposition) of the signals sent out from the revolution speed sensors 21a, 21b can be carried out by a simple circuit, and also only one harness for supplying the synthesized signal is required. Also, the calculation of the revolution speeds n ca , n cb every rolling elements 9a, 9b in both rows is not required of the calculator that receives the synthesized signal. That is, the difference between the revolution speeds n ca , n cb can be sensed directly. For this reason, as described above, reduction in the full length of the harness and reduction in an amount of computation in the calculator portion can be achieved.
  • a synthesized signal shown in FIG.16B is obtained by synthesizing (superposing) the signals sent out from the revolution speed sensors 21a, 21b and shown in FIG .16A respectively.
  • This synthesized signal is changed by a period T 2 .
  • This change (change in a pulse width) is generated by a difference between the signals fed from the revolution speed sensors 21a, 21b, and a reciprocal (1/T 2 , frequency) of the change period T 2 gives a difference in frequencies of the signals sent out from the revolution speed sensors 21a, 21b.
  • the difference ⁇ n C b-n ca " between the revolution speeds n ca , n C b of the rolling elements 9a, 9b in both rows is calculated by the change period T 2 or the frequency, and then the axial load F a applied between the outer ring 1 and the hub 2 is calculated based on the ratio " (n C b-n C a) /ni" of the difference M n cb -n ca to the rotational speed n ⁇ of the hub 2.
  • This case is similar to the case that the signals are changed like a sine wave,- except that the swell period Ti is replaced with the change period
  • FIG.17 shows a second embodiment of the present invention.
  • the revolution speed encoder 26a also the revolution speed- encoder 26b shown in FIGS .1 and 2
  • the revolution speeds of the rolling elements canbe sensed precisely by providing a plurality of revolution speed sensors 21a ⁇ , 21a 2 (two in FIG.17) . Therefore, in the case of the present embodiment, the revolution speed sensors 21a ⁇ , 21a 2 are arranged to deviate from the revolution direction of the rolling elements 9a, 9b (see FIG.l ⁇ whose revolution speeds are to be sensed. More particularly, the revolution speed sensors 21a ⁇ , 21a 2 are arranged in opposite positions with respect to a rotation center 0 2 of the hub 2 (see FIG.l) by 180 degree.
  • the present embodiment is constructed to eliminate the influence of an error caused by the eccentric motion of the revolution speed encoder 26a by adding the sensed signals of the revolution speed sensors 21a ⁇ , 21a 2 . This respect will be explained with reference to FIGS.18 to 20 in addition to FIG.17.
  • a clearance required to hold rotatably these rolling elements 9a, 9b is provided between an inner surface of a pocket of the retainer 22a, in which the revolution speed encoder 26a is held (or the retainer itself has a function as the encoder) , and the rolling contact surfaces of the rolling elements 9a, 9b. Therefore, no matter how an assembling precision of respective constituent members is enhanced highly, it is possible that a rotation center 0 22 of the retainer 22a is deviated from a center 0 2 of a pitch circle of the rolling elements
  • an eccentricity ⁇ affects the sensed signal of the revolution speed sensor, the sensing surface of which is opposed toasidesurfaceof the revolution speed encoder 26a.
  • the revolution speed represented by the output signal of the revolution speed sensor 21a is changed like a sine wave, as indicated by a broken line ⁇ . More particularly, in case the moving velocity in the horizontal direction in FIG.19 is added to the moving velocity in the rotation direction, the output signal gives a signal that corresponds to the velocity that is quicker than the actual revolution speed. Conversely, in case the moving velocity in the horizontal direction in FIG.19 is subtracted from the moving velocity in the rotation direction, the output signal gives a signal that corresponds to the velocity that is slower than the actual revolution speed.
  • FIG.19 depicts an eccentricity in an exaggerated fashion rather than the actual case.
  • a pair of revolution speed sensors 21a ⁇ , 21a 2 are provided. Therefore, as shown in FIG.17, in case a rotation center O 22 of the retainer 22a is deviated from the center of a pitch circle of the rolling elements 9a, 9b (rotation center of the hub 2) , in other words, in case the retainer 22a performs a whirling motion due to an eccentricity, the revolution speed of the rolling elements 9a, 9b can be sensed precisely. That is, the revolution speed sensors 21a ⁇ , 21a 2 arranged in the opposite positions by 180 degree with respect to a center 0 2 of the pitch circle are affected in the reverse direction by the same amount.
  • the revolution speed of the rolling elements 9a, 9b can be measured precisely independent of the whirling motion generated due to the eccentricity. Also, in order to execute the control of the vehicle stability more strictly, the load applied to the rolling bearing unit can be sensed precisely.
  • the technology to correct the error generated by the eccentric motion of the retainer by arranging a plurality of revolution speed sensors in equal interval positions in the circumferential direction of the revolution direction of the rolling elements can be applied to any bearing unit as well as the double row rolling bearing unit used to support the wheels, as shown in FIG.1.
  • such technology can be applied to a single row deep groove or angular contact ball bearing.
  • a plurality of rolling elements 9, 9 are provided between an outer ring raceway 29 and an inner ring raceway 30, which are formed on mutually opposing peripheral surfaces of an outer ring 27 and an inner ring 28 arranged in a concentric fashion respectively, and is used in- a state that the contact angles and the enough preload are applied (in a state that the preload is never lost in operation) .
  • sensing surfaces of a pair of revolution speed sensors 21a ⁇ , 21a 2 fitted to a cover 31, which is fitted/fixed to an outer periphery of the outer ring 27, are opposed to a side surface of a revolution speed encoders 26 coupled to a retainer 22 in the opposite positions with respect to a rotation center of the inner ring 28 by 180 degree.
  • the rolling bearing unit in which the rolling elements are provided in double rows and to which the present invention is applied, is used in a state that the rotational speed of the rotating ring is always constant like the rotation supporting portion of the machine tool or the carrier car in the factory
  • the radial load F r can be detected exactly by using only a sum v n c +n ca " " or a product "n ca Xn C b" of the revolution speeds n ca , n C b of the rolling elements 9a, 9b in both rows.
  • the axial load F a can be detected exactly by using only the difference fl n C b-n ca " of the revolution speeds.
  • the inexpensive speed sensors used widely to get the control signal of the ABS or the TCS in the related art can be used as the revolution speed sensors 21a, 21b used to measure the revolution speeds n ca , n c of the rolling elements 9a, 9b in double rows and the rotational speed sensor 15b used to measure the rotational speed of the hub 2.
  • the overall load measuring system for the rolling bearing unit can be constructed inexpensively.
  • the revolution speeds of the rolling elements 9a, 9b in double rows are measured as the rotational speeds of the retainers 22a, 22b holding the rolling elements 9a, 9b in double rows is explained.
  • the revolution speeds of the rolling elements 9a, 9b in double rows can be measured directly.
  • the magnetic sensors are used as the revolution speed sensors 21a, 21b and the elements made of magnetic material is used as the rolling elements 9a, 9b in double rows, characteristics of the magnetic sensors constituting the revolution speed sensors 21a, 21b are changed-with the revolution of the rolling elements 9a, 9b in double rows (in the case of the active sensor into which the magnetic sensors are incorporated) .
  • a quantity of magnetic flux flowing through the magnetic sensors is increased at an instance when the rolling elements 9a, 9b made of magnetic material are present in vicinity of the sensing surfaces of the revolution speed sensors 21a, 21b, while a quantity of magnetic flux flowing through the magnetic sensors is reduced at an instance when the sensing surfaces are opposed to adjacent portions located between the rolling elements 9a, 9b in the circumferential direction.
  • a frequency at which the characteristics of the magnetic sensors are changed in answer to the change in the quantity of magnetic flux flowing through the magnetic sensors is proportional to the revolution speed of the rolling elements 9a, 9b in double rows.
  • the revolution speed can be derived based on the sensed signals of the revolution speed sensors 21a, 21b into which the magnetic sensors are incorporated.
  • the rolling elements 9a, 9b in double rows must be made of the magnetic material. Therefore, when the elements made of non-magnetic material such as ceramics, or the like are used as the rolling elements 9a, 9b in double rows, optical sensors must be used as the revolution speed sensors 21a, 21b.
  • a grease to lubricate the rolling contact portions is sealed in a space 32 into which the sensing portions of the revolution speed sensors 21a, 21b are inserted (see FIGS .1 and 2 ) , and thus the light is not effectively reflected in such cases.
  • the elements made of magnetic material should be used as the rolling elements 9a, 9b in double rows and also the sensors into which the magnetic sensors are incorporated should be used as the revolution speed sensors 21a, 21b. Also, as described above, it is preferable that, when the revolution speed of the rolling elements 9a, 9b in double rows is directly measured by the revolution speed sensors 21a, 21b, the retainers made of non-magnetic material such as synthetic resin, or the like should be used as the retainers 22a, 22b to hold the rolling elements 9a, 9b in double rows.
  • the revolution speed of the rolling elements 9a, 9b in double rows can be measured exactly by using the retainers 22a, 22b made of non-magnetic material.
  • the retainers 22a, 22b may be made of non-magnetic metal such as copper alloy, or the like, but more preferably the retainers made of synthetic resin should be employed because such retainers are light in weight and are difficult to cut off the magnetic fluxes.
  • the austenite- based stainless steel that is normally known as the non-magnetic metal has also minute magnetism, such steel is disadvantageous to sense exactly the revolution speed.
  • the ceramics is lighter in weight than the hard metal such as bearing steel, the stainless steel, or the like, which is normally utilized to construct the rolling elements 9a, 9b, and has a smaller centrifugal force as well as a smaller inertial mass both acting in operation.
  • the revolution speeds n ca , n ch of the rolling elements 9a, 9b in double rows are changed exactly to correspond to the change in the rotational speed ni of the hub 2.
  • the radial load F r and the axial load F a applied to the rolling bearing unit can be measured exactly based on the rotational speed ni and the revolution speeds n ca , n cb .
  • the technology to measure exactly the revolution speed of the rolling elements while suppressing the revolution slip by forming the rolling elements of the ceramics in this way can be applied to not only the case that the rolling elements are formed of elements except the balls but also the case of the single row rolling bearing unit instead of the double row type.
  • the passive magnetic revolution sensor in which a coil is wound around a pole piece made of magnetic material canbeused. Inthiscase, a voltage of the sensed signal of the passive magnetic revolution sensor is lowered when the rotational speed becomes slow.
  • the load measuring device for the rolling bearing unit as the object of the present invention, because such device intends to implement the running stability during the high-speed running of the mobile body as a major object, reduction of the voltage of the sensed signal during the low-speed running is hard to become an issue. Accordingly, if the inexpensive passive sensor is employed as one or plural sensors out of respective sensors 21a, 21b, 15b, reduction in a cost of the overall device can be achieved. In this case, it is preferable that, if a high- precision control during the low-speed running is also intended, the active revolution sensor into which the magnetic sensors are incorporated should be used as described above.
  • the magnetism sensing element such as Hall element, etc.
  • sensor constituent parts such as permanent magnet, yoke (pole piece), coil, etc. should be molded in a holder made of non-magnetic material such as synthetic resin, or the like except the sensing surfaces at the top end portion.
  • the sensing portions of the revolution sensor constructed by molding the sensor constituent parts in the synthetic resin are opposed to the sensed portions, i.e., of the revolution speed encoders 26a, 26b fitted to the rolling elements 9a, 9b in double rows or the retainers 22a, 22b in the case of the revolution speed sensors 21a, 21b or the rotational speed encoder 13a in the case of the rotational speed sensor 15b, respectively.
  • the above sensors 21a, 21b, 15b are held in one holder, the operation of fitting these sensors 21a, 21b, 15b into the outer ring 1 can be facilitated.
  • these sensors 21a, 21b, 15b may be fitted separately to non-rotated portions according to the applications.
  • the signals sensed by the revolution speed sensors 21a, 21b to represent the revolution speed of the rolling elements 9a, 9b in double rows and the signal sensed by the rotational speed sensor 15b to represent the rotational speed of the hub 2 may be processed by the hardware such as analog circuit, or the like or the software using the microcomputer, or the like.
  • the present invention is applied to the double row angular contact rolling bearing unit used to support the wheel of the vehicle is explained. But the present invention may be applied to the normal double row or multiple row ball bearing or tapered roller bearing.
  • the loads applied to the rolling bearing unit are calculated by sensing the revolution speed in remaining rows in addition to the revolution speed of the rolling elements in two rows. Also-, when the present invention is applied to the double row tapered roller bearing in which tapered rollers are used as the rolling elements, an amount of change in the revolution speed becomes smaller than the double row ball bearing, nevertheless the load can be calculated based on change in the revolution speed of the tapered rollers.
  • the present invention can be implemented in any hub unit as well as so-called third- generation hub unit in which the ' outside inner ring raceway 8 is formed on the outer peripheral surface of the hub main body 4 in the middle portion, as shown in FIG .1.
  • the present invention may be applied to the so-called second- generation hub unit, in which a pair of inner rings are fitted/fixed to the middle portion or the inner end portion of the hub main body, and the so-called first-generation hub unit, in which a pair of inner rings are fitted/fixed to the middle portion or the inner end portion of the hub main body and also the outer ring whose outer periphery is shaped into a mere cylinder is inserted/supported into the supporting hole of the knuckle.
  • the present invention may be applied to the structure in which a pair of rolling bearings each serving as the single row rolling bearing respectively are provided between an outer peripheral surface of the hub main body in the middle portion or the inner end portion and an inner peripheral surface of the supporting hole of the knuckle to construct the double row rolling bearing unit.
  • the application of the present invention is not limited to the hub unit for the idler wheel as shown, and the present invention may be applied to the hub unit for the driving wheel (rear wheels of FR car, RR car, MR car, front wheels of FF car, and all wheels of 4WD car) , as shown in above FIGS.38 to 40.
  • the revolution speeds n ca , n C b of the rolling elements 9a, 9b in double rows are measured in the course of measuring the radial load F r and the axial load F a . Then, if these revolution speeds n ca , n cb in respective rows are detected, the contact angles ( a a , ⁇ b ) can be calculated based on above Eq. (1) . Therefore, if the contact angles are monitored, an alarm unit for generating an alarm at the time of abnormal state by grasping the state of the rolling bearing unit can be constructed.
  • the case the preload to the rolling bearing unit is lost (the preload escapement occurs ⁇ , the case the excessive axial load F a is loaded to the rolling bearing unit, etc. may be considered, for example.
  • the preload out of them is lost, contact angles become small.
  • vibrations or noises caused due to the shake are generated, and in addition wears of the rolling contact surfaces of the rolling elements 9a, 9b in double rows and the outer ring raceway 7 and the inner ring raceway 8 are advanced because of the revolution slip.
  • the excessive axial load F a is applied, the contact angle in any row is increased.
  • the circuit shown in FIG.22 is constructed to generate the alarm about the concerned row by monitoring the contact angles a , ⁇ b of the rolling elements 9a, 9b in double rows respectively when the contact angles a , ⁇ b of the rolling elements 9a, 9b in any one row are deviated from the normal value by a predetermined value or more. For this reason, the rotational speed ni of the hub 2 being fed from the rotational speed sensor 15b, the revolution speed n ca , n cb of the rolling elements 9a, 9b in double rows being fed from the revolution speed sensors 21a, 21b, and specifications of the rolling bearing unit being stored in a memory 34 are input into an arithmetic circuit 33.
  • Various values necessary for calculation of the contact angles a , h of the rolling elements 9a, 9b in respective rows such as a pitch circle diameter D of the rolling elements 9a, 9b in double rows, a diameter d of these rolling elements 9a, 9b, etc. as well as an initial contact angle 0 of the rolling elements 9a, 9b in respective rows are stored in the memory 34 by inputting the model number of the rolling bearing unit or inputting directly the necessary values.
  • the arithmetic circuit 33 calculates the contact angles a , b of the rolling elements 9a, 9b in respective rows based on respective speed n i ⁇ n ca , n cb and respective diameters D, d, and then feeds them to comparators 35a, 35b. These comparators 35a, 35b compare the contact angles a a , a, of the rolling elements 9a, 9b in respective rows with the initial contact angle 0 fed from the memory 34 at a time point of calculation. Then, it is decided whether or not the contact, angles a , ⁇ b of the rolling elements 9a, 9b in respective rows are within the normal range. If it is decided that such contact angles ⁇ a , b are out of the normal range (abnormal), alarms 36a, 36b are caused to generate the alarm.
  • the approach to decide whether or not the operation state of the rolling bearing unit is proper is not limited to the step of comparing the contact angles ⁇ a , h of the rolling elements 9a, 9b in respective rows with the initial contact angle QJO. Any approach may be carried out. For example, it is possible to decide whether or not the operation state of the rolling bearing unit is proper, by detecting an elastic deformation amount ⁇ , the radial load F r , the axial load F a , and contact stiffness K of the rolling bearing unit and then comparing them with the specifications of the rolling bearing unit. In this case, the arithmetic circuit 33 executes calculations given by Eqs. (2) to (5) .
  • FIG.23 shows a fifth embodiment of the present invention.
  • one rotational speed sensor 15b is positioned closer to the outer peripheral surface of the hub 2 than apair of revolution speed sensors 21a, 21b.
  • three sensors 21a, 21b, 15b are separated mutually and the magnetic interference among these sensors 21a, 21b, 15b is reduced . Since such magnetic interference is suppressed small, improvement in the reliability of sensing the revolution speed and the rotational speed and in turn the reliability of calculation of the load can be achieved.
  • FIG.24 shows an sixth embodiment of the present invention.
  • positions of three sensors 21a, 21b, 15b provided to the top end portion 24 of the sensor unit 23 are shifted more largely than the case of above fifth embodiment.
  • the sensors21a, 21b, 15b packaged in the IC package are aligned closer mutually in series with the axial direction of the sensor unit 23. By doing this, the magnetic interference among these sensors 21a, 21b, 15b is suppressed smaller and also a diameter of the sensor unit 23 is made small.
  • FIG.25 shows an seventh embodiment of the present invention.
  • a connector 37 is provided on the outer peripheral surface of the outer ring 1, and a plug 39 provided to one end portion of a harness 38 used to output the sensed signals of the sensors 21a, 21b, 15b can be connected to this connector 37.
  • the other end of the harness 38 is coupled to a controller provided to the vehicle body.
  • damage of the harness 38 can be prevented by employing such structure.
  • the connector 37 provided to the outer ring 1 side may be provided separately from the sensor unit 23, as show in FIG.25, and also may be provided integrally with a sensor unit 23a, as show in FIG.27.
  • FIG.28 shows an eighth embodiment of the present invention.
  • an inner diameter a of the revolution speed encoder 26a (26b) attached to the side surface of the rim portion 25 of the retainer 22a (22b) is set larger than an inner diameter A of the side surface of the rim portion 25, while an outer diameter b of the same revolution speed encoder 26a (26b) is set smaller than an outer diameter B of the side surface of the rim portion 25 (A ⁇ a ⁇ b ⁇ B) . Since dimensions of respective portions are defined in this manner, such an event can be prevented that the revolution speed encoder 26a (26b) comes into contact with the inner peripheral surface of the outer ring 1 and the outer peripheral surface of the hub 2 (see FIGS.l and 2, for example) .
  • FIGS.29 and30 shows a ninth embodiment of the present invention.
  • a rotational speed encoder 13b used to sense the rotational speed of the hub 2 and the rotational speed sensor 15b are provided to the inner endportion of the rolling bearing unit. Only the revolution speed encoders 26a, 26b and the revolution speed sensors 21a, 21b are provided between the rolling elements 9a, 9b aligned in two rows.
  • the rotational speed encoder 13b may be fitted/fixed independently to the inner end portion of the hub 2, as shown in FIG.29, or may be attached to a side surface of a slinger 40 constituting a combination sealing ring, as shown in FIG.30.
  • the rotational speed sensor 15b may be fitted/fixed to the cover 14 that is put on the opening portion at the inner end of the outer ring 1, as shown in FIG.29, or may be fitted/fixed directly to the outer ring 1, as shown in FIG.30.
  • the gear such as the permanent magnet, the magnetic material, or the like may be used as respective encoders 13b, 26a, 26b
  • the magnetic sensor such as the active type, the passive type, or the like may be used as respective sensors 21a, 21b, 15b
  • the calculator used to calculate the load may be provided to the rolling bearing unit or may be provided separately from the rolling bearing unit, and so forth.
  • FIG.31 shows a tenth embodiment of the present invention. As described above, if the revolution speed encoder is omitted by sensing directly the passing of the rolling element, a lower cost can be achieved.
  • the present embodiment intends to implement such structure.
  • each of the revolution speed sensors 21a, 21b has magnetic sensing elements 41 provided to oppose to the rolling elements 9a, 9b respectively, and a permanent magnet 42 put ' between the magnetic sensing elements 41 and provided on the opposite side to the rolling elements 9a, 9b respectively.
  • These rolling elements 9a, 9b are made of magnetic material such as the bearing steal, or the like.
  • a quantity of magnetic fluxes passing through the magnetic sensing elements 41 is increased at an instance when the rolling elements 9a, 9b pass in vicinity of the magnetic sensing elements 41, while a quantity of magnetic fluxes passing through the magnetic sensing elements 41 is decreased while the rolling elements 9a, 9b are positioned at remote portions from the magnetic sensing elements 41. Also, since characteristics of the magnetic sensing elements 41 are changed based on the change in this quantity of magnetic fluxes, the revolution speed of the rolling elements 9a, 9b can be measured by measuring a period of such change of the characteristics (or a frequency) .
  • these rolling elements 9a, 9b are made of non-magnetic material such as ceramics, or the like, a density of the magnetic fluxes passing through the magnetic sensing elements 41 can be changed with the revolution motion of the rolling elements 9a, 9bbyplating magnetic material on the surface, embedding the magnetic material in the inside of the ceramics, or the- like.
  • the revolution speed sensors 21a, 21b are arranged between the rows of the rolling elements 9a, 9b. But fitted positions of the revolution speed sensors 21a, 21b are not limited to the space between these rows.
  • the revolution speed sensors 21a, 21b maybe provided at both end positions of the outer ring 1 in the axial direction to put the rolling elements 9a, 9b from both sides in the axial direction .
  • structures of the rotational speed encoder 13a and the rotational speed sensor 15b used to sense the rotational speed of the hub 2 are not particularly limited. Like the above embodiments, various structures known in the related art can be employed.
  • FIGS.32 and 33 show an eleventh embodiment of the present invention.
  • the passive magnetic sensor since at least one sensor out of the rotational speed sensor 15b and the revolution speed sensors 21a, 21b is constructed by the passive magnetic sensor, reduction in a cost is intended.
  • the active type magnetic sensor is used as respective sensors 15b, 21a, 21b constituting the loadmeasuring device, such s ructure has an advantage that the rotational speed and in turn the load can be measured stably from a low speed to a high speed, but such a problem exists that a cost of the magnetic sensor is slightly increased.
  • the passive type magnetic sensor which is constructed by winding a coil 44 round a yoke 43 (same meaning as a stator or a pole piece) made of magnetic material, as at least any one sensor out of respective sensors 15b, 21a, 21b.
  • the revolution speed sensors 21a, 21b shown in FIG.32 may be selected or the rotational speed sensor 15b shown in FIG.33 may be selected.
  • the rotational speed sensor 15b is formed of the active type magnetic sensor in the structure shown in FIG.32, while a pair of revolution speed sensors 21a, 21b are formed of the active type magnetic sensor in the structure shown in FIG.33.
  • the permanent magnet is not provided on the sensor side when the encoder is formed of the permanent magnet.
  • the encoder is made of mere magnetic material (not the permanent magnet) and the magnetic characteristic is changed alternately at an equal interval along the circumferential direction.
  • a structure of the passive type magnetic sensor is not particularly restricted and a variety of structures such as stick type, ring-like type, or the like, known in the related art may be used.
  • it is selected in response to the requiredperformance that the revolution speed sensors 21a, 21b shown in FIG.32 should be selected as the passive type magnetic sensor or that the rotational speed sensor 15b shown in FIG.33 should be selected as the passive type magnetic sensor
  • the revolution speed sensors 21a, 21b shown in FIG.32 should be constructed as the passive type magnetic sensor .
  • the passive type magnetic sensor since the axial load is generated when the revolution speed of the rolling elements 9a, 9b is high such as the lane change during the high-speed traveling, or the like, in many cases there is caused no problem in practical use even though the passive type magnetic sensor whose output voltage becomes low during the low-speed running is used as the revolution speed sensors 21a, 21b.
  • FIGS.34 to 36 show a twelfth embodiment of the present invention.
  • at least one sensor out of the revolution speed sensors 21a, 21b and the rotational speed sensor 15b is constructed as a resolver.
  • the resolver is composed of rotors 45 fixed to members such as the retainers 22a, 22b, the hub 2, etc. to sense the rotational speed, and stators 46 fitted/fixed to the fixed outer ring 1 directly or via the cover 14 in a state that such stators are arranged concentrically with the rotors 45 around the rotors 45.
  • the rotors 45 may be composed of an eccentric rotor.
  • such rotor is composed of a- elliptical rotor, a triangle riceball type, or the like, to- have a point-symmetrical shape, not only imbalance of the rotation can be reduced but also the number of pulses per revolution can be increased.
  • the revolution speed can be measured precisely up to the low-speed range, nevertheless the ' number of times of change in the output of the magnetic sensor per one revolution of the encoder is reduced and therefore a resolving power in the velocity sensing is not always enhanced.
  • the resolver is used as the speed sensor, the number of times of change in the output (number of pulses) per one revolution of the rotors 45 can be increased rather than the active type magnetic sensor, and a resolving power in the velocity sensing is enhanced and in turn a responsibility of the load calculation can be accelerated.
  • the resolver main body is constructed only by a coil and a core (stator) , the structure can be made simple and the reliability can be easily assured.
  • a sensed signal of the resolver is input into an R/D converter and then taken out as a pulse signal that is changed at a frequency that is in proportion to the speed.
  • one of the revolution speed sensors 21a, 21b and the rotational speed sensor 15b should be constructed as the resolver.
  • the rotational speeds of a pair of retainers 22a, 22b are sensed by the resolver and also the rotational speed of the hub 2 is sensed by the magnetic sensor.
  • the rotational speed of the hub 2 is sensed by the resolver and also the rotational speeds of a pair of retainers 22a, 22b are sensed by the magnetic sensor.
  • the rotational speeds of a pair of retainers 22a, 22b and the rotational speed of the hub 2 are sensed by the resolver.
  • the event that structures of the resolver and the magnetic sensors and their fitted positions are not limited to those illustrated, the event that a variety of materials for the rotor and the encoder can be employed, etc. are similar to the case in foregoing embodiments.
  • the axial load applied to the rolling bearing unit can be calculated based on a ratio of the revolution speeds of the rolling elements in double rows independent of change in the rotational speed of the hub.
  • the rotational speed of the hub is not needed in load calculation.
  • the sensor for sensing the rotational speed of the hub which is needed to control the ABS or the TCS, can be omitted. More particularly, if an average value of the revolution speeds of the rolling elements in double rows is used as the rotational speed of the hub, a precision enough to control the ABS or the TCS in practical use can be assured.
  • an action of the axial load may be considered as a factor for changing the revolution speeds of the rolling elements in double rows.
  • a measuring precision of the rotational speed is never degraded to such an extent that the precision becomes an issue in practical use.
  • the reason for this is that, as described above, even if the revolution speed in one row is increased by the axial load, the revolution speed in the other row is changed toward the smaller direction.
  • the revolution speeds in double rows are also changed by the radial load, but such change is- small in contrast to the influence of the axial load. Therefore, in some case such change canbe neglected according to the precision required to control the ABS or the TCS.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)
  • Rolling Contact Bearings (AREA)
PCT/JP2004/006410 2003-05-22 2004-05-06 Load measuring device for rolling bearing unit and load masuring rolling bearing unit WO2004104545A1 (en)

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US10/535,936 US7320257B2 (en) 2003-05-22 2004-05-06 Load measuring device for rolling bearing unit and load measuring rolling bearing unit
EP04731482.8A EP1625376B1 (en) 2003-05-22 2004-05-06 Load measuring device for rolling bearing unit and load measuring rolling bearing unit

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JP2003-144942 2003-05-22
JP2003144942 2003-05-22
JP2003171715 2003-06-17
JP2003-171715 2003-06-17
JP2003172483 2003-06-17
JP2003-172483 2003-06-17
JP2004007655A JP4517648B2 (ja) 2003-05-22 2004-01-15 転がり軸受ユニットの荷重測定装置
JP2004-007655 2004-01-15

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CN102331349B (zh) * 2011-06-17 2013-06-12 武汉理工大学 永磁轴承刚度测量装置
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JP6676982B2 (ja) * 2016-01-27 2020-04-08 株式会社ジェイテクト 転がり軸受装置および転がり軸受の異常の検出方法
CN106441898B (zh) * 2016-10-27 2019-05-31 天津大学 一种滚动轴承回转精度的测试装置
DE102017109540A1 (de) 2017-05-04 2018-03-01 Schaeffler Technologies AG & Co. KG Wälzlageranordnung mit Sensoreinrichtung
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CN101706364B (zh) * 2009-11-19 2011-06-15 晋西铁路车辆有限责任公司 对铁路货车轮对上的轴承进行磨合检测的装置
US9011013B2 (en) 2011-05-09 2015-04-21 Ntn Corporation Sensor-equipped wheel bearing

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KR20050092388A (ko) 2005-09-21
JP4517648B2 (ja) 2010-08-04
KR100860642B1 (ko) 2008-09-26
JP2005031063A (ja) 2005-02-03
EP1625376B1 (en) 2016-11-23
US7320257B2 (en) 2008-01-22
EP1625376A1 (en) 2006-02-15
US20060070462A1 (en) 2006-04-06

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